CN104884811B - For with temperature about control the valve of at least one hydraulic load - Google Patents
For with temperature about control the valve of at least one hydraulic load Download PDFInfo
- Publication number
- CN104884811B CN104884811B CN201380069293.2A CN201380069293A CN104884811B CN 104884811 B CN104884811 B CN 104884811B CN 201380069293 A CN201380069293 A CN 201380069293A CN 104884811 B CN104884811 B CN 104884811B
- Authority
- CN
- China
- Prior art keywords
- piston
- temperature
- valve
- fluid
- interface
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/004—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying driving speed
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D23/00—Control of temperature
- G05D23/01—Control of temperature without auxiliary power
- G05D23/02—Control of temperature without auxiliary power with sensing element expanding and contracting in response to changes of temperature
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Temperature-Responsive Valves (AREA)
- Fluid-Pressure Circuits (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid Mechanics (AREA)
- Sliding Valves (AREA)
- Multiple-Way Valves (AREA)
Abstract
For with temperature about control the valve (10) of at least one hydraulic load, the valve includes：Valve chest (12), the valve chest have at least one fuel tank interface (T), at least one working interface (A) and at least one supply interface (P)；The control piston (30) for being used to control the interface (A, P, T) by accumulator such as working spring (74) pretension being movably disposed in the valve chest (12)；And can by with can be predetermined temperature (TFluid) fluid loading temperature-sensitive element (62), the temperature-sensitive element couples according to effect and the control piston (30), wherein, the control piston is by being movable in control pressure present on the supply interface (P), and the temperature-sensitive element (62) and the accumulator (74) mating reaction so that the temperature-sensitive element causes the change relevant with temperature of the pretightning force acted on the control piston (30).
Description
Technical field
The present invention relates to it is a kind of be used for temperature about control the valve of at least one hydraulic load, the valve includes：Valve
Housing, the valve chest have at least one fuel tank interface, at least one working interface and at least one supply interface；In the valve
The control piston for being used to control the interface by accumulator such as working spring pretension being movably disposed in housing；With
And the temperature-sensitive element that can be loaded by the fluid with temperature that can be predetermined, the temperature-sensitive element is according to effect and the control piston coupling
Connection.In addition, the present invention relates to a kind of hydraulic system, the hydraulic system includes at least one such valve.
Background technology
Changed in hydraulic system and convey energy, loss is produced in the energy conversion and energy conveying.Herein
It will can mechanically and hydraulically be converted to heat.The task of cooling device is, heat is exported from hydraulic system.Cooling device leads to
Blower fan typically can by hydraulic-driven, wherein, driving hydraulic means for the hydraulic motor of arranging be configured to independently of
Want the loop of itself in the loop of cooling fluid.
A kind of valve for starting the type as known in rear disclosed DE 10 2,012 008 480.3.Known valve is used for
The hydraulic unit driver of ventilator is controled according to the temperature for the fluid to be cooled down, more accurately predetermined vent machine rotating speed.Valve and by this
The ventilation blower driver that valve controls is arranged in a common hydraulic circuit.Valves known is with the slow of small regulation dynamic
It is bluntHydraulic system in application also allow improve space.In addition it is desirable that, limit by the predetermined control of valve
Therefore pressing pressure simultaneously can protect temperature-sensitive element from overload.
The content of the invention
The task of the present invention is, the application of extension valve, is particularly expanded to the slow of small regulation dynamic
Blunt hydraulic system, and enable the valve to improve the function that its method of operation reaches other.
Solved according to the task of the invention by a kind of following valve, the valve has the spy according to the present invention on the whole
Sign：For with temperature about control the valve of at least one hydraulic load, the valve includes：Valve chest, the valve chest have
At least one fuel tank interface, at least one working interface and at least one supply interface；In the valve chest movably
The control piston for being used to control the interface by accumulator pretension set；And can by with can be predetermined temperature
The temperature-sensitive element of fluid loading, the temperature-sensitive element couple according to effect and the control piston, wherein, the control piston passes through
It is movable in control pressure present on the supply interface, and the temperature-sensitive element matches somebody with somebody cooperation with the accumulator
With so that the temperature-sensitive element causes the change relevant with temperature of the pretightning force acted on the control piston, and its feature exists
In the tune relevant with temperature that the choke piston in the valve chest passes through the regulating element of temperature-sensitive element or the temperature-sensitive element
Section motion can move so that the choke piston is according to the regulation motion release between the supply interface and fuel tank interface
With temperature rising, what is increased passes through cross section.
Therefore present invention provide that, temperature-sensitive element and control piston are the components of two separation, and they can be with valve chest
It is arranged in a common fluid space.Temperature-sensitive element (the also referred to as hot operation element) medium for example to be cooled down by fluid institute
Inflow, circulation or percolation and the temperature for being equal to (annehmen) described fluid.Rise with the temperature of fluid, temperature-sensitive element draws
Play motion, compression or the expansion of accumulator and correspondingly cause the change of the pretension of the accumulator, the pretension is predetermined to be passed through
Control piston (also referred to as main control piston) pressure to be adjusted.By application be typically configured as compression spring accumulator,
That is, working spring realizes the application of the valve according to the present invention, it is blunt with small regulation dynamic to be particularly used to adjusting
Hydraulic system.Also it can be used for according to the solution of the present invention but definitely the application compared with high dynamic.
In a preferred implementing form according to the valve of the present invention, it is provided between temperature-sensitive element and control piston
Moveable choke piston in valve chest, the choke piston act on connection preferably via regulating element in side and temperature-sensitive element and
Opposite side and accumulator effect connection, particularly connect, wherein, accumulator its away from choke piston end on control
Piston effect connection, particularly it is connected with the control piston.Advantageously, being formed on temperature-sensitive element has regulating element, such as
Tappet, stroke, Yi Jiyan are produced in the case of power of the tappet with fluid temperature (F.T.) rising at the same time on choke piston is increased
The motion of action direction, also referred to as adjusts displacement.More precisely, advantageously, regulating element abut on choke piston and
The choke piston is moved according to its regulation displacement relevant with temperature.Regulation displacement and affiliated power pass through choke piston transmission
Onto accumulator.
It is also advantageous that the P-T by supply interface to fuel tank interface that can be controled by choke piston is fluidly connected and formed
In valve chest, and choke piston fluidly connects according to the regulation displacement locking or at least partly release P-T of temperature-sensitive element.Grip
Stream piston is by adjusting displacement, discharging gripping by the increase of supply interface to fuel tank interface in other words by the stroke of temperature-sensitive element
Flow cross section.Fluidly connected to typically constitute by the P-A of supply interface to working interface and lived in the control as main control piston
Beyond the Great Wall, the operating pressure to be adjusted is present on the working interface.
According to the present invention valve another preferred embodiment in, provided with it is at least one arrange interface to supply, it is excellent
It is selected in the input choke valve set in valve chest at least one arrange to the fluid components of supply interface.In input choke valve
On pressure differential increased according to the chokes cross section of chokes valve piston and improved, and in hydraulic system of the arranging to hydraulic load
In system pressure must exceedingly (ü berproportional) raise, so as to maintain control piston on dynamic balance.Cause
The pressure-temperature characteristic curve that the script of this desired dynamic characteristic is linear can be for example matched with exceedingly (such as with three
Power) elevated fan characteristic curve.
It is also advantageous that temperature-sensitive element its with the end that deviates from of control piston with overloading element, such as overload spring
Connect it is preferred that being acted on compression spring, be particularly attached thereto, wherein, overload element is limited to act on to control by accumulation of energy part and lived
Power beyond the Great Wall or pretension.In this manner it is achieved that so realize that a kind of pressure limits so that exceed maximum permissible value in system pressure
In the case of control that piston is integral with temperature-sensitive element by choke piston, and the pressure to be adjusted is acted in temperature-sensitive element
On overload element.The pressure to be adjusted is limited to by the predetermined value of overload element and therefore protects temperature-sensitive element from overload.
In terms of the constituted mode of the control piston of valve, preferably it is arranged such so that control piston exists as differential piston
There is main piston part and second piston part, second piston part has different compared to main piston part rise on common piston rod
The piston area of effect, main piston part and second piston part limit first fluid space therebetween, supply interface be passed into this
In one fluid space, wherein, main piston part by means of control seamed edge or control breach come control the first fluid space with
Pass through cross section between working interface.
In addition, it can be provided with valve chest by the connecting line in first fluid space to choke piston and by the chokes
Piston leads to the branch line of fuel tank interface, wherein, the fluid passage between connecting line and branch line can be by means of gripping
Piston is flowed to control.
Furthermore being formed in the valve chest has in external fluid if the fluid of predetermined temperature on temperature-sensitive element
Fluid path between interface, and temperature-sensitive element is arranged in the fluid path, then produce following possibility, i.e. can be with
The autonomous valve run with not having outer fluid line namely according to the present invention.It is also advantageous that provided with by temperature-sensitive
The fluid that element leads to fuel tank interface leads back to portion, and the fluid portion of leading back to preferably equally extends in valve chest.Fluid introduction part and
The fluid portion of leading back to forms a kind of rinse fluid art passage of inside of the temperature loading for temperature-sensitive element.
Alternatively, the fluid for predetermined temperature-sensitive component temperature can be formed in valve chest and had between outside fluid interface
Fluid path, wherein, temperature-sensitive element set in the fluid path.External fluid interface is used in the alternative, wherein
Fluid or leading back to for rinse fluid art are not internally by valve or pump case but in outside progress.
The structural form of fluid loading or temperature loading with temperature-sensitive element independently, can be formed at least in valve chest
One external fluid interface arranged to temperature-sensitive element.
The present invention also relates to a kind of hydraulic system, the hydraulic system includes at least one hydraulic load and at least one pressed
According to the present invention be used for temperature about control the valve of at least one hydraulic load, the hydraulic load is connected to the valve
On working interface, wherein, control piston is at least partly discharged according to the temperature of temperature-sensitive element or locking is by supply interface to work
The P-A of interface is fluidly connected.
Here, at least one hydraulic load can be arranged to hydraulic motor, the hydraulic motor forms one together with regulation pump
Hydraulic system, particularly Motor-pump unit, wherein, corresponding hydraulic load preferably influences to adjust by the feedback of operating pressure
Save the conveying capacity of pump, particularly make a reservation for its angle of oscillation.Preferably according in the hydraulic system of the present invention, realizing hydraulic motor simultaneously
Therefore the relevant with temperature of its motor power controls.Based on being determined by function at least one, the preferably multiple spring of application, spy
The compression spring that is not preferably connected in series and realize the relevant with temperature of the blunt system with small regulation dynamic
Regulation.In the embodiment according to the hydraulic system of the present invention, corresponding hydraulic load is advantageously formed to adjust cylinder, should
Regulation cylinder is connected on the working interface of valve and the angle of oscillation of the piston predetermined adjustment pump of the regulation cylinder in active side.
In another preferred implementing form according to the hydraulic system of the present invention, the ventilation of fluid motor-driven cooling device
Machine, the cooling device have by the predetermined ventilation blower rotating speed of hydraulic system.There is provided to have herein according to the present invention and be used for ventilation blower
The axial poiston pump of the integrated temperature control valve (TCV) of driver, without using electrically or electronically element.
Brief description of the drawings
Additional advantages of the present invention and feature are drawn by accompanying drawing and the following drawings.Feature that is foregoing and further enumerating
Accordingly individually or mutually it can be realized in any combination according to the present invention.Be shown in the drawings be characterized in pure signal and
It should not be construed as proportionally.In figure：
Fig. 1 is shown according to the first embodiment of the valve of the present invention and with the hydraulic system of the arranging shown in symbol view
Sectional view, wherein, the active operating state of system is shown under the cold state of fluid；
Fig. 2 is shown as regulation displacement-temperature characteristics of the temperature-sensitive element of a part for the valve according to the present invention；
Fig. 3 shows system pressure-temperature characteristics of the valve according to the present invention；
Fig. 4 shows the view shown in more schematically simplifying strongly relative to Fig. 1, this view show that first embodiment
Inactive running status；
Fig. 5 shows the view according to Fig. 4, this view show that the activity operation shape in the fluid to be cooled down of heat
State；
Fig. 6 shows the view according to Figure 4 and 5, this view show that overload when pressure cut off running status；
Fig. 7 partly shows the second embodiment of the valve according to the present invention with sectional view and partly with symbol view,
Wherein, inactive running status is shown；
Fig. 8 show second embodiment compared to Fig. 7 further schematically simplify shown in view, wherein, show
Active operating state in the case of cold fluid；
Fig. 9 shows the corresponding views of second embodiment, wherein, show the operation shape with the hot fluid to be cooled down
State；And
Figure 10 shows the corresponding views of second embodiment, wherein, showing has the operation of pressure cut off in overload
State.
Embodiment
Partly shown in Fig. 1 with sectional view, partly with symbol view according to valve solution of the invention
First embodiment.There is valve chest 12 with 10 valves represented as entirety, the valve chest is made up of three parts 14,16 and 18,
These three parts can realize clear assembling of the valve chest 12 along the separation point position 20 extended vertically accordingly.In view of simplify
View is not illustrated in detail connection solution.Line of vision towards the valve 10 according to Fig. 1 is looked, and is existed on the downside of valve chest 12
Supply or pump interface P, work use interface A and fuel tank interface T, and the fuel tank interface has tank pressure or environmental pressure.
In addition, the line of vision towards Fig. 1 is looked and two fluid interfaces 22,24 on the left side of valve housing portion 16 be present, the two fluids connect
Mouth can be flowed in the direction of the arrow by the fluid of such as hydraulic pressure oil form.
Two fluid spaces 26,28 set in succession be present in its longitudinal direction extension of the interior edge of valve housing portion 18.
Control piston be present with being guided with can moving longitudinally in described two fluid spaces 26,28 and in the inwall of valve chest 12
30.Have three with being in axial direction spaced from each other distance according to according to Fig. 1 view on the piston rod 32 of the control piston
The individual piston piece 34,36 and 38 widened in diametrically relative to piston rod 32.Two annulars or the piston cylindrically formed
Part 34,36 has same overall diameter, and piston piece 38 accordingly reduces in diametrically on the other hand, so as in fluid
Moved in space 28, the fluid space correspondingly equally reduces in terms of its overall diameter relative to fluid space 26.Fluid space
28 form a kind of spring compartment, and the accumulator in the form of compression spring 40 is accommodated in the spring compartment.According to the present invention
Solution but can also be realized completely in the case of no compression spring 40.
On the piston rod 32 according to the view according to Fig. 1 is on the right side of it is axially projecting in piston piece 38 when, the piston rod
Thus in its free end side form stop surface 39, for the opening position can with valve chest 12 in a row in
Wall is reclined.But piston piece 34 is directly translated into opposed side upper piston rod 32, the piston piece is according to the phase according to Fig. 1
It should be abutted in the view of the cold operation state of valve solution on stop part 42, the stop part 42 is formed in the following way,
So that another fluid space 44 is configured to smaller in diametrically compared to adjacent fluid space 26, so as to thus exist
Diameter leap be present in valve housing portion 16, the valve housing portion is relative to valve housing portion 18 in the separation extended vertically
Position 20, which is formed, convex shoulder, and the convex shoulder is used as being used for the stop part 42 for entirely controlling piston 30, as long as the stop part is as shown in Figure 1
It is located at like that in its left stop dog position.
Another piston piece 46 is connected with the left piston part 34 of control piston 30, another piston piece is in diametrically phase
Ground is answered to be directed with can moving longitudinally in other fluid space 44 with reducing relative to control piston 30.What is originally shown
In embodiment, another piston piece 46 be control piston 30 single type part and along convex shoulder 20 in diameter side
Face reduces；It is also envisaged that run through piston rod 32 and mutually construct described two piston pieces 38 single type
With 46.Line of vision towards Fig. 1 is looked, and another piston piece 46 is upper to the left to have stop part 48, and the stop part is according to piston apparatus
Shift position in valve chest can with to be reclined with the stop surface of the side of 50 choke pistons represented.Choke piston 50
Guide with being moved longitudinally in fluid space 44 and there are two annular piston pieces 52,54, the two piston piece edges
Axial direction is looked mutually keeps interval by being arranged on the piston rod piece 56 of centre.Following choke piston 50 is preferably configured as
Single type.
Valve gear figure 1 illustrates cold running status under, choke piston 50 is with the free end side of left piston 52
Abut on another stop part 58, another stop part again produce by as caused by by the 4th fluid space 60 reduced diameter portion
Raw, axial direction of the 4th fluid space along piston apparatus is looked the end of the piston piece 52 on the right side of it by choke piston 50
Lateral spacing is fixed and is limited on its another opposed side by temperature-sensitive element 62.In addition axial direction side of the 4th fluid space 60 along valve 10
To looking, the regulating element 64 that is belonging to temperature-sensitive element 62 passes through.
Temperature-sensitive element 62 is contained in valve housing portion 16 in element receiving portion 66；But according to the operation shape of valve 10
State, temperature-sensitive element 62 can against another accumulator in the form of another compression spring 68 effect along towards Fig. 1 line of vision to
Move left, wherein, temperature-sensitive element 62 then has interval in its right free end side relative to stop surface 70, and this hereinafter goes back
It will be described with.Otherwise another compression spring 68 is supported on temperature-sensitive element 62 and another at its on one free end
It is supported on one free end on the inner side of valve chest part 14, the valve chest part outwards closes valve chest in the form of seal bootr
12.In addition, temperature-sensitive element 62 is surrounded by doughnut 72, fluid interface 22,24 is led in the doughnut.
Another the 3rd accumulator with spring form is extended between choke piston 50 and another piston piece 46, should
Compression spring is hereinafter represented with working spring 74.As Fig. 1 is additionally illustrated, supply or pump interface P and work
Interface A is at least partly led in first fluid space 26, and the first fluid space is by two piston pieces 36,38 in edge lateral spacing
It is fixed.The first fluid space 26 that fuel tank interface T is led in the region between two piston pieces 34 and 36 of control piston 30 again
In.Connecting line is passed through between the such part extended between two piston pieces 36 and 38 in first fluid space 26
76, the connecting line leads to the through valve chest 12 in the upper area of valve chest and with its other end along the longitudinal direction
In three fluid spaces 44, that is, in following region, the region is limited by two piston pieces 52 and 54 of choke piston 50.But
Connecting line 76 can replace being arranged on (being not shown for valve chest 12 in upper area according to the structural form on construction
) in lower area.It is provided with other the with being extended in parallel on the downside of valve chest 12 and vertically with connecting line 76
Two connecting lines 78, second connecting line are led in fuel tank interface T and with its another free end with one free end
Lead in the 4th fluid space 60.In addition the branch line 80,82 that extends laterally be present, the branch line is from the second connecting line
78 start on the one hand to lead in working spring space 84 that (working spring 74 prolongs in the working spring space by branch line 80
Stretch) and on the one hand by branch line 82 towards the 3rd fluid space 44, wherein, in the valve according to the view according to Fig. 1
Under cold operation state, the piston piece 54 that following second branched pipe road 82 is choked piston 50 is completely covered.
In addition as shown in figure 1, being connected with the regulation cylinder 86 for being configured to cylinder with differential effect on valve 10, this hereinafter will also enter one
Step illustrates, wherein, adjust cylinder 86 piston 88 in cylinder housing in the usual manner by piston space 90 and piston rod space 92
Separate Fluid Sealing.Back-moving spring 96 is provided with the piston rod space 92 passed through by control-rod 94, the control-rod is again preferred
Ground is controled as the part of the single type of piston 88 by the piston, and the back-moving spring attempts to make piston towards the direction of its relaxation
88 move from right to left along the line of vision towards Fig. 1.The control-rod 94 for being configured to piston rod combines regulation or the adjustment composition regulation of cylinder 98
The governor motion (angle of oscillation SW) of pump 98, the regulation pump are for example configured to axial piston machine.Motor 100 may be used as using
In the driver of regulation pump 98, the motor can be constant motor but can also be the motor of variable speed.Instead of electricity
Motivation can also use other driving sources.For regulation existing capability describe by the constant driving rotating speed of pump, wherein,
Actual operation is not absolute precondition.Regulation pump 98 takes out hydraulic fluid from fuel tank T and the hydraulic fluid exists
Output end can provide towards pump interface P via crossover location 102 and therefore be supplied to valve, wherein, baffle plate or the conduct of choke valve 106
Pressure differential or input choke valve are switched in following intake line 104.Guiding fluidly connects tune since crossover location 102
The piston rod space 92 of cylinder 86 is saved, and hydraulic motor 108 is connected with the opposite side of crossover location 102, the hydraulic motor
As ventilation blower driver and drive with the ventilating vane 110 of rotor configurations.Transported by regulation pump 98 by hydraulic motor 108
Defeated fluid is discharged to fuel tank side T again.By the caused air mass flow percolation heat exchanger in the usual manner of ventilating vane 110
112, it is for example configured to plate heat exchanger, and hydraulic circuit 114 is connected with the heat exchanger, the hydraulic circuit for example with
In operating hydraulic equipment not shown further, and temperature controllable, can particularly cool down the hydraulic equipment by
In the fluid that another pump installation not shown further conveys via heat exchanger 112.Hydraulic circuit 114 can be by one not
The guiding device further shown is connected to first fluid interface 22 in input side and is connected to the second of valve 10 in outlet side
Body interface 24；But there is also following possibility, pass through the first and second fluid interfaces 22,24 in the fluid circuit of separation
To reduce temperature, the running temperature situation that the fluid interface only indirectly reflects in hydraulic circuit 114.Except these are referred to
Conducting element, regulation cylinder 86 piston space 90 working interface A is connected to by another connecting line 116.
Before the function of the valve solution shown is expanded on further, it should be noted that exist for clear function
Compression spring 40 can also be saved in second fluid space 28, and according to shown in schematic diagram, buffering choke valve 118 connects
Fluidly connecting in portion between interface A and fuel tank interface T is used in valve chest 12.Fluid space 28 should be towards fuel tank
Side T releases, this is not shown.
In order to illustrate functional mode with reference first to Fig. 4, valve 10 shown in this figure and the hydraulic system that arranges it is non-live
Dynamic running status.In this system pressure p0=0, because adjusting pump 98 in the case of the drive motor of shut-off or motor 100
Driving rotating speed nAn=0.As shown in figure 4, regulation pump 98 is adjusted according to full volume flow herein, that is to say, that regulation pump 98
Angle of oscillation SW is maximum.This composition is maintained at right side by working spring 74 herein for the control piston 30 of differential area piston
A-T positions, the piston space 90 for adjusting so as to working interface A and therefore cylinder 86 are connected with fuel tank interface T.Based on foundation and work
The fuel tank connection in space 90 is filled in, the piston 88 guided in regulating piston 90 is maintained at it corresponding to maximum by back-moving spring 96
On angle of oscillation SW position.Back-moving spring 96 in cylinder 86 is adjusted be present is not to force needs for the function, because adjusting
Section system also can definitely be realized in the case of no spring reset.In addition, between working interface A and fuel tank interface T
Persistently connect through and exist in valve chest 12 via the connection that buffering choke valve 118 is formed.According to the minimum temperature of fluid
TFluidThe power that=min causes the regulation displacement S=min of the regulating element 64 of temperature-sensitive element 62 and acted on choke piston 50
F=min is minimized, and preferably equal to zero.Therefore control piston 30 substantially keeps constant in its A-T position.Arranging to heat
On the side of quick element 62, choke piston 50 is reduced under inactive running status with being abutted in the inside of valve chest 12 with diameter
On the stop part 58 (referring to Fig. 5) of the form in portion.
If system is changed into active operating state by inactive state, then with rated speed nANDriving regulation pump 98.
Based on also cold fluid, power F=f (S there is no by temperature-sensitive element 62min) be applied on choke piston 50, so as to which this is gripped
Connecting line 76 and 78 is separated from each other by stream piston by the control seamed edge of closing.The system pressure built on supply interface P
P0Therefore decline not over connecting line 76 and therefore with can predetermined intensity act on control piston 30 differential pressure
Face, the control piston is moved against working spring 74 by the total power of caused hydraulic pressure and thus discharges P-A connections, such as in Fig. 1
Shown in.The volume flow as caused by the pressure drop between interface P and working interface A is supplied is together with implementation on differential piston
Regulating piston 88 is induced to the power on big piston area jointly.If the power has exceeded in piston rod side pressure-loaded and therefore
The power effect of smaller piston ring surface, then regulating piston 88 is carried out towards its movement of end position that right side is looked in Fig. 1.
As this result, cause that the volume of the piston rod side of regulation cylinder 86 is minimum first, the conveying capacity for thus adjusting pump 98 subtracts first
It is small to change angle of oscillation SW towards the direction of small value to minimum, its mode for the piston 88 of regulation cylinder 86.
Caused system pressure P0Substantially correspond to the power of the working spring of pretension relatively weakly and pump-regulating mechanism
The summation of the adjusting force needed and in the ideal case be located at for drive ventilation blower 10 hydraulic motor 108 starting institute
Under the minimum pressure needed.The regulating element 64 of temperature-sensitive element 62 is grown with its minimal adjustment in the fluid with low temperature
Degree, that is, the regulating element are moved fully into.FminIt is the power as caused by minimal adjustment length, the power acts on choke piston 50
The upper and power substantially can be assumed to be zero in the case where fluid is without the cold state limited in more detail.This anticipates for choke piston 50
Taste：The choke piston does not change it relative to the initial of the inactive running status according to Fig. 4 in the case of cold fluid
Position, so as to which pipeline 76 and 78 is separated from each other as described above by the control seamed edge of closing.The change of state is gone out due to fluid
Existing temperature rise is just realized.
The state figure 5 illustrates.According to the elevated temperature T of fluidFluidProduce temperature-sensitive element 62 and its regulating element 64
Elevated regulation displacement and therefore generate the corresponding movement of choke piston 50.
Regulation displacement-temperature characteristics shown in figure 2 of temperature-sensitive element 62 should illustrate temperature-sensitive element 62
Function and show with normal regulating displacement SregFirst area, the normal regulating displacement with the first gradient herein almost
It is 1 linearly with the temperature T of fluidFluidRise；Further it is shown that then there is abnormal regulation displacement Sover
Two regions, the abnormal regulation displacement is with the second gradient for reducing compared to the first gradient linearly with the temperature T of fluidFluid
Rise until maximum.Normal regulating displacement SregAt this corresponding to temperature-sensitive element 62 or its regulating element 64 in adjustment region
Stroke, correspondingly abnormal regulation displacement SoverCorresponding to being out of the line for temperature-sensitive element 62 or its regulating element being attached thereto 64
Journey.
The extension of the regulation displacement of the regulating element 64 of the temperature-sensitive element 62 according to caused by being raised by fluid temperature (F.T.) is produced
The movement of raw choke piston 50, so as to produce the pretension improved on control piston 30 by working spring 74.Working spring 74
Increase the control piston 30 that moves right in Fig. 5 of power, thus the control seamed edge on piston piece 36 increasingly reduce from confession
Arrive to working interface A and further the P-A of piston space 90 of regulation cylinder 86 to interface P and fluidly connect, thus adjust cylinder 86
The angle of oscillation SW of the motion of piston 88 increasingly increase regulation pump 98, correspondingly to improve conveying capacity.Meanwhile choke piston 50
By means of increasingly being discharged between the connecting line 78 of connecting line 76 and second positioned at the control seamed edge on piston piece 54
Connection, second connecting line lead to fuel tank interface T.Thus reduce and make after choke valve 106 is inputted in fluid space 26
The control pressure on control piston 30 is used, this expression：Regulation pump 98 on the pressure side on the system pressure P that has0Must mistake
Degree ground rise, to maintain the dynamic balance on control piston 30.Originally thus linear pressure-temperature characteristic curve is such as being schemed
It is not linear as being illustrated in 3, but is matched with the elevated fan characteristic curve of cube, referring to Fig. 3.In the figure
In the operating point of inactive system is indicated with I, operating point of the activity system in the case of cold fluid is indicated with II, and with III
Indicate the operating point in adjustment region in the case of hot fluid.As can be seen, compared to according to line pressure
Control pressure P1, need additional pressure P due to declining by the pressure of choke piston 502Deposited to maintain in adjustable range
Control pressure.Produced as the temperature of fluid rises by accordingly the ventilation blower rotating speed as caused by hydraulic motor 108 is improved
Raw system pressure P0Corresponding rise.
Fig. 6 shows a kind of running status, wherein, system pressure P0It is increased to a value for corresponding to overload.
This pressure that control piston 30 is acted on present in fluid space 26 produces the left side of sensing in figure 6 of a following intensity
Piston force, in the intensity lower piston with its stop part 48 (referring to Fig. 1) and integral (the auf Block of choke piston 50
Gehen), in other words abut on choke piston 50, so as to pressure be applied to via choke piston 50 on regulating element 64 and after
And it is applied on temperature-sensitive element 62.The overload of temperature-sensitive element 62 however avoid in the following way, i.e. support temperature-sensitive element 62
Another spring 68 is used as overload protection arrangement, and the overload protection arrangement can realize the motion of the compliance of temperature-sensitive element 62.Exist simultaneously
On the position corresponding to overload for controlling piston 30, the P-A connections on valve chest 12 are practically without being choked, so as to
Move the piston 88 of regulation cylinder 86 for pressure cut off, to make the angle of oscillation SW of regulation pump 98 towards the side of minimum delivery amount
Cause to motion and thus pressure cut off.Shown in figure 3 on pressure-temperature characteristic curve with IV and reaching overload shape
Operating point during state.
Fig. 7 to 9 shows second embodiment.The difference of the embodiment and first example is, is provided with valve chest 12
Internal fluid introduction part, the stream that the fluid introduction part of the inside passes through the interface 22 by supply interface P to temperature-sensitive element 62
Body pipeline 27 and the second connecting line 78 is reached by return line 29 by the interface and therefore reaches fuel tank interface T.Cause
To be thus provided with the interior flushing fluid circuit of the fluid for predetermined temperature-sensitive component temperature, so can alternatively save temperature-sensitive
The external interface 22 of element in itself, as the external interface is shown in the figure.If it is expected the complete self-sufficiency of ventilation blower driver certainly
Foot operation, then internal flow connection is thus a kind of alternative for external interface.Internal flow pipeline 27 passes through
It is connected by input choke valve 31 with supply interface P, and the second input choke valve 33 positioned at supply interface P and is adjacent to piston piece
Between 38 fluid space.Compared to first example another difference is that, after interface P is supplied formed control fluid with adjust
The separation of throttling body, its mode are that control piston 30 has intermediate piston part between the piston piece 38 and piston piece 36 of side
35, the intermediate piston part has the piston area with the effect of the identical of piston piece 36.Led to by the fluid components 37 of supply interface P branches
Enter into the fluid space 26 between piston piece 36 and intermediate piston part 35.In fluid space 26 control is acted on as controling power
Control pressure on piston 30 processed with the fluid components 37 of branch in a manner of being controlled by piston piece 36 on working interface A
Such separation between existing regulation pressure opens following possibility, i.e., is worked with following control pressure, the control pressure
Power is under the minimal adjustment pressure that regulation cylinder 86 needs.It is to control the spring hardness of the small needs on piston 30 and corresponding
Relatively low control pressure can realize less control oil consumption and realize efficiency damage smaller in regulating valve as noted above
Lose.
In addition, the functional mode of second embodiment corresponds to the functional mode of first embodiment, so that need not to this
Further inquire into.
Claims (14)
1. for temperature about control the valve (10) of at least one hydraulic load, the valve includes：Valve chest (12), it is described
Valve chest has at least one fuel tank interface (T), at least one working interface (A) and at least one supply interface (P)；Institute
State be movably disposed in valve chest (12) by accumulator pretension be used for control the fuel tank interface (T), working interface
(A) and supply interface (P) control piston (30)；And can be by with the predetermined temperature (T of energyFluid) fluid loading
Temperature-sensitive element (62), the temperature-sensitive element according to effect with it is described control piston (30) couple, wherein, the control piston by
Control pressure present on the supply interface (P) is movable, and the temperature-sensitive element (62) is matched somebody with somebody with the accumulator
Cooperation is used so that and the temperature-sensitive element causes the change relevant with temperature of the pretightning force acted on the control piston (30),
Characterized in that, the regulation that the choke piston (50) in the valve chest (12) passes through temperature-sensitive element (62) or the temperature-sensitive element
The regulation campaign relevant with temperature of element (64) can move so that the choke piston is according to the regulation motion release described
Supply interface (P) and fuel tank interface (T) between with temperature rise and increase pass through cross section.
2. valve according to claim 1, it is characterised in that the accumulator is working spring (74).
3. valve according to claim 2, it is characterised in that the choke piston (50) abuts in temperature-sensitive element in side
(62) on regulating element (64) and on the end that opposite side abuts in working spring (74), the working spring is with it
The other end is abutted on control piston (30) for generation pretightning force.
4. the valve according to one of claims 1 to 3, it is characterised in that at least one input choke valve (106；31st, 33) set
Put for carrying out chokes to the fluid for the supply interface (P) that flows.
5. the valve according to one of claims 1 to 3, it is characterised in that the temperature-sensitive element (62) deviates from the control at it
Supported on the end of piston (30) processed by overloading element.
6. valve according to claim 5, it is characterised in that the overload element is compression spring (68).
7. the valve according to one of claims 1 to 3, it is characterised in that the control piston (30) exists as differential piston
There is main piston part (36) and second piston part (38), the second piston part has compared to institute on common piston rod (32)
The different piston area to work of main piston part (36) is stated, the main piston part and second piston part limit first therebetween
Fluid space (26), the supply interface (P) are passed into the first fluid space；And the main piston part (36) by
In control seamed edge or control breach come control between the first fluid space (26) and working interface (A) by transversal
Face.
8. valve according to claim 7, it is characterised in that be provided with the valve chest (12) by first fluid space
(26) branch line of the fuel tank interface (T) is led to the connecting line (76) of choke piston (50) and by the choke piston
(80、82)；And the fluid passage between the connecting line (76) and the branch line (80,82) can be by means of described
Choke piston (50) controls.
9. the valve according to one of claims 1 to 3, it is characterised in that be the predetermined temperature on the temperature-sensitive element (62)
(TFluid) fluid and the fluid path having between outside fluid interface (22,24) is formed in the valve chest (12), and
And the temperature-sensitive element (62) is arranged in the fluid path.
10. valve according to claim 9, it is characterised in that in valve chest (12), it is described supply interface (P) with
Fluid circuit (27) is provided between first fluid interface (22) on the temperature-sensitive element (62).
11. hydraulic system, the hydraulic system include at least one hydraulic load and it is at least one according to claim 1 to 10 it
Described in one be used for temperature about control the valve (10) of at least one hydraulic load, the hydraulic load is connected to the valve
(10) on working interface (A), wherein, the control piston (30) of the valve (10) is according to the temperature on the temperature-sensitive element (62)
Spend (TFluid) and at least part discharges or locking is by the connection for supplying interface (P) to working interface (A).
12. hydraulic system according to claim 11, it is characterised in that the hydraulic system, which has, to be arranged to the hydraulic pressure
The Motor-pump unit of load, the Motor-pump unit have regulation pump (98) and hydraulic motor (108), wherein, the hydraulic pressure
The conveying capacity by influenceing the regulation pump (98) in the feedback of operating pressure present on the working interface (A) is loaded,
Its mode is that the hydraulic load makes a reservation for its angle of oscillation (SW).
13. hydraulic system according to claim 12, it is characterised in that the hydraulic load is configured to adjust cylinder (86),
The angle of oscillation (SW) of the predetermined regulation pump (98) of piston (88) of the regulation cylinder, wherein, the piston of the regulation cylinder (86)
Space (90) is connected with the working interface (A), and the piston rod space (92) of the regulation cylinder (86) and the regulation pump
(98) on the pressure side connection, the regulation pump guiding system pressure, the system pressure pass through the supply interface (P) and input
Choke valve (106) works in the first fluid space (26) of the valve (10) as control pressure.
14. the hydraulic system according to claim 12 or 13, it is characterised in that hydraulic motor (108) the driving ventilation
Machine (110), the ventilation blower are used for the heat exchanger (112) that cooling belongs to hydraulic circuit (114).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013000121.8 | 2013-01-04 | ||
| DE102013000121.8A DE102013000121A1 (en) | 2013-01-04 | 2013-01-04 | Valve for temperature-dependent control of at least one hydraulic consumer |
| PCT/EP2013/003936 WO2014106535A1 (en) | 2013-01-04 | 2013-12-21 | Valve for the temperature-dependent control of at least one hydraulic load |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104884811A CN104884811A (en) | 2015-09-02 |
| CN104884811B true CN104884811B (en) | 2017-12-19 |
Family
ID=50031290
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380069293.2A Expired - Fee Related CN104884811B (en) | 2013-01-04 | 2013-12-21 | For with temperature about control the valve of at least one hydraulic load |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US9920778B2 (en) |
| EP (1) | EP2941571A1 (en) |
| JP (1) | JP6321679B2 (en) |
| CN (1) | CN104884811B (en) |
| AU (1) | AU2013372034B2 (en) |
| CA (1) | CA2893301A1 (en) |
| DE (1) | DE102013000121A1 (en) |
| HK (1) | HK1210250A1 (en) |
| WO (1) | WO2014106535A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3069798B1 (en) * | 2015-03-17 | 2019-08-14 | Wacker Neuson Produktion GmbH & Co. KG | Control device for vibration generators for ground compacting devices |
| DE102015010849A1 (en) * | 2015-08-20 | 2017-02-23 | Hydac Fluidtechnik Gmbh | Valve device for controlling a fluid flow and flow control valve |
| KR102399571B1 (en) * | 2015-09-09 | 2022-05-19 | 삼성디스플레이 주식회사 | Display apparatus and method of driving the same |
| US10678276B2 (en) | 2016-11-16 | 2020-06-09 | Hydac Fluidtechnik Gmbh | Valve device for controlling a fluid flow and flow control valve |
| US10633827B2 (en) * | 2017-10-16 | 2020-04-28 | Deere & Company | Temperature responsive hydraulic derate |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4699571A (en) * | 1984-11-28 | 1987-10-13 | Mannesmann Rexroth Gmbh | Control valve for a variable displacement pump |
| US5800130A (en) * | 1996-12-19 | 1998-09-01 | Caterpillar Inc. | Pressure control system for a variable displacement hydraulic pump |
Family Cites Families (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3359831A (en) * | 1965-05-20 | 1967-12-26 | Gen Motors Corp | Multiple speed fan drive |
| US3913831A (en) * | 1974-03-22 | 1975-10-21 | Deere & Co | Oil cooler bypass valve |
| US4062329A (en) * | 1976-07-29 | 1977-12-13 | The United States Of America As Represented By The Secretary Of The Army | Fan drive system |
| JPS6025020Y2 (en) * | 1982-03-31 | 1985-07-26 | アイシン精機株式会社 | thermo valve |
| DE3407747A1 (en) * | 1984-03-02 | 1985-09-12 | Robert Bosch Gmbh, 7000 Stuttgart | Pressure regulator for an adjustable pump |
| RU2055221C1 (en) * | 1993-06-09 | 1996-02-27 | Московская государственная академия автомобильного и тракторного машиностроения | Drive of internal combustion engine cooling system fan |
| DE19601376A1 (en) * | 1996-01-16 | 1997-07-17 | Rexroth Mannesmann Gmbh | Sensor circuit |
| US5876185A (en) * | 1996-11-20 | 1999-03-02 | Caterpillar Inc. | Load sensing pump control for a variable displacement pump |
| US5778693A (en) * | 1996-12-20 | 1998-07-14 | Itt Automotive Electrical Systems, Inc. | Automotive hydraulic engine cooling system with thermostatic control by hydraulic actuation |
| JPH10212951A (en) * | 1997-01-30 | 1998-08-11 | Nissan Diesel Motor Co Ltd | Hydraulic control type fan driving system |
| KR20030067942A (en) * | 2002-02-09 | 2003-08-19 | 현대자동차주식회사 | Electronic thermostat using variable control system |
| JP2005163920A (en) * | 2003-12-03 | 2005-06-23 | Sanwa Seiki Co Ltd | Hydraulic fan driving device |
| JP5202727B2 (en) * | 2009-03-24 | 2013-06-05 | 株式会社小松製作所 | Cooling fan driving device and fan rotation speed control method |
| DE102010007247B4 (en) * | 2010-02-09 | 2019-02-14 | Hydac Filtertechnik Gmbh | Hydraulic fan drive |
| CA2822480C (en) * | 2010-12-23 | 2018-09-25 | Dana Canada Corporation | Valve apparatus |
| DE102012008480A1 (en) | 2012-04-26 | 2013-10-31 | Hydac Cooling Gmbh | cooler |
-
2013
- 2013-01-04 DE DE102013000121.8A patent/DE102013000121A1/en not_active Ceased
- 2013-12-21 US US14/648,929 patent/US9920778B2/en not_active Expired - Fee Related
- 2013-12-21 JP JP2015551140A patent/JP6321679B2/en active Active
- 2013-12-21 AU AU2013372034A patent/AU2013372034B2/en not_active Ceased
- 2013-12-21 CA CA2893301A patent/CA2893301A1/en not_active Abandoned
- 2013-12-21 CN CN201380069293.2A patent/CN104884811B/en not_active Expired - Fee Related
- 2013-12-21 EP EP13826733.1A patent/EP2941571A1/en not_active Withdrawn
- 2013-12-21 WO PCT/EP2013/003936 patent/WO2014106535A1/en active Application Filing
-
2015
- 2015-11-03 HK HK15110859.2A patent/HK1210250A1/en unknown
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4699571A (en) * | 1984-11-28 | 1987-10-13 | Mannesmann Rexroth Gmbh | Control valve for a variable displacement pump |
| US5800130A (en) * | 1996-12-19 | 1998-09-01 | Caterpillar Inc. | Pressure control system for a variable displacement hydraulic pump |
Also Published As
| Publication number | Publication date |
|---|---|
| AU2013372034A1 (en) | 2015-05-28 |
| WO2014106535A1 (en) | 2014-07-10 |
| JP2016502058A (en) | 2016-01-21 |
| CN104884811A (en) | 2015-09-02 |
| DE102013000121A1 (en) | 2014-07-10 |
| EP2941571A1 (en) | 2015-11-11 |
| US9920778B2 (en) | 2018-03-20 |
| AU2013372034B2 (en) | 2017-04-20 |
| CA2893301A1 (en) | 2014-07-10 |
| JP6321679B2 (en) | 2018-05-09 |
| US20150308468A1 (en) | 2015-10-29 |
| HK1210250A1 (en) | 2016-04-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104884811B (en) | For with temperature about control the valve of at least one hydraulic load | |
| US11156146B2 (en) | Electric coolant pump | |
| US9581072B2 (en) | Motor vehicle engine cooling system and method | |
| JP5539525B2 (en) | Fuel supply circuit for aero engines | |
| CN101849096B (en) | Fuel overflow valve for a fuel injection system, and fuel injection system having a fuel overflow valve | |
| US9790840B2 (en) | Fluid flow control device and method | |
| WO2008132858A1 (en) | Hydraulic control unit | |
| CN104653272A (en) | Cooling system | |
| KR20190057389A (en) | Internal combustion engine | |
| CN101120213A (en) | Refrigeration plant | |
| CN103477090B (en) | Electronic infinite step controller actuator | |
| CN103867285B (en) | retarder cooling system | |
| CA2691461C (en) | Two-stage heat exchanger with interstage bypass | |
| US10119435B2 (en) | Combustion engine and mantle assembly therefore | |
| CN107923278A (en) | Electromagnetic relief pressure valve | |
| JP2015536429A (en) | Device for controlling the drive of a cooling device ventilator that can be driven by a fluid pressure motor | |
| CN105020113B (en) | Convertible fluids flow hydraulic pump | |
| US8534059B2 (en) | Pressure reducing gas storage device, air-jet system, and motor vehicle | |
| US7975481B2 (en) | Method and apparatus for controlling a steam cycle | |
| CN103867617A (en) | Commercial vehicle thermostat for arranging hydraulic retarder | |
| JP5266150B2 (en) | Hydraulic circuit for high pressure hydraulic system | |
| US10710728B2 (en) | Device for determining at least one of a degree of opening of an air opening and a cross section of an air duct connected to the opening | |
| US20140205425A1 (en) | Oil cooling arrangement and method of cooling oil | |
| CN110107433A (en) | A kind of diesel engine air inlet system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| REG | Reference to a national code |
Ref country code: HK Ref legal event code: DE Ref document number: 1210250 Country of ref document: HK |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20171219 Termination date: 20181221 |
|
| REG | Reference to a national code |
Ref country code: HK Ref legal event code: WD Ref document number: 1210250 Country of ref document: HK |